TWM494744U - Assembly for bicycle - Google Patents

Description

Bicycle component

The present invention relates to a bicycle assembly.

In a conventional bicycle component such as a speed change mechanism or a drive unit, a planetary gear mechanism is used in order to decelerate the rotation from the input member (refer to Patent Document 1).

The planetary gear mechanism has a sun gear, a plurality of planetary gears, a ring gear, and a carrier. The planet gear meshes with the sun gear. The ring gear meshes with a plurality of planet gears. The carrier is free to rotatably hold the planet gears about the axis of rotation of the sun gear. In the case where the planetary gear mechanism is actuated, as shown in Fig. 8, the planetary gears, the sun gear and the ring gear are alternately alternately engaged with one tooth and two teeth. As shown in Fig. 9A, the engagement of the planetary gears (e.g., three planetary gears) with the sun gear and the ring gear is simultaneously switched from one tooth engagement to two tooth engagement or from two tooth engagement to one tooth engagement.

[Advanced technical literature] [Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open Publication No. 2014-37203

In the conventional planetary gear mechanism, as shown in Figs. 8 and 9A, the meshing of the planetary gears, the sun gear and the ring gear are simultaneously switched from one tooth engagement to two tooth engagement or from two tooth engagement. To a tooth engagement. Therefore, when a tooth engagement is switched with the engagement of the two teeth, vibration may occur in the bicycle component.

In view of the above problems, the present invention aims to provide a bicycle assembly that can reduce vibration.

The bicycle assembly of the present invention includes a sun gear, a plurality of planetary gears, a ring gear, and a carrier. The plurality of planet gears mesh with the sun gear. The ring gear meshes with a plurality of planet gears. The carrier is free to rotatably hold the planet gears about the axis of rotation of the sun gear.

Here, the value obtained by adding the number of teeth of the sun gear to the number of teeth of the ring gear divided by the number of the planetary gears is an integer. The number of teeth of the sun gear and the number of teeth of the ring gear are different from the integer multiple of the number of the planetary gears.

According to the bicycle assembly of the present invention, the timing at which the number of meshes of the planetary gears changes can be made different by satisfying the above conditions. That is to say, the number of meshes of the respective planetary gears can be changed at different phases. Thereby, the vibration at the time of changing the meshing number of the planetary gear can be reduced as compared with the conventional technique. That is Said, can reduce the vibration of the bicycle components.

The bicycle assembly of the present invention can also be constructed as follows. In the bicycle assembly of the present invention, the number of planetary gears is three. Thereby, the vibration of the bicycle component can be reduced with a minimum configuration.

The bicycle assembly of the present invention can also be constructed as follows. In the bicycle assembly of the present invention, the number of teeth of the planetary gear is a value that is an integral multiple of the number of the planetary gears. Even if this condition is further increased, the vibration of the bicycle component can be reduced.

The bicycle assembly of the present invention can also be constructed as follows. In the bicycle module of the present invention, the planetary gear includes a first planetary gear and a second planetary gear. The second planetary gear has a larger diameter than the first planetary gear. The sun gear has a first sun gear. The first sun gear meshes with the first planetary gear.

Here, the value obtained by adding the number of teeth of the first sun gear to the number of teeth of the ring gear divided by the number of the first planetary gears is an integer. The number of teeth of the first sun gear and the number of teeth of the ring gear are different from the value of an integral multiple of the number of the first planetary gears.

According to the bicycle assembly of the present invention, the timing at which the number of meshing of each of the first planetary gears changes can be made different by satisfying the above conditions. In other words, the number of meshes of the respective first planetary gears can be changed in different phases. Thereby, the vibration at the time of changing the meshing number of the first planetary gear can be reduced as compared with the conventional technique. That is to say, the vibration of the bicycle component can be reduced.

The bicycle assembly of the present invention can also be constructed as follows. In the bicycle assembly of the present invention, the sun gear further has a second sun tooth wheel. The second sun gear has a smaller diameter than the first sun gear and meshes with the second planetary gear. Here, the value obtained by adding the number of teeth of the second sun gear to the number of teeth of the ring gear divided by the number of the second planetary gears is an integer. The number of teeth of the second sun gear and the number of teeth of the ring gear are different from the value of an integral multiple of the number of the second planetary gears.

When the condition is further increased, as in the case of the first planetary gear described above, the vibration at the time of the change in the meshing number of the second planetary gear can be further reduced. That is to say, the vibration of the bicycle component can be more effectively reduced.

The bicycle assembly of the present invention can also be constructed as follows. In the bicycle module of the present invention, the planetary gear includes a first planetary gear and a second planetary gear. The second planetary gear has a smaller diameter than the first planetary gear. The sun gear has a first sun gear. The first sun gear meshes with the first planetary gear.

Here, the value obtained by adding the number of teeth of the first sun gear to the number of teeth of the ring gear divided by the number of the first planetary gears is an integer. The number of teeth of the first sun gear and the number of teeth of the ring gear are different from the value of an integral multiple of the number of the first planetary gears. Here, the value obtained by adding the number of teeth of the second sun gear to the number of teeth of the ring gear divided by the number of the first planetary gears is an integer. The number of teeth of the second sun gear and the number of teeth of the ring gear are different from the value of an integral multiple of the number of the second planetary gears.

In the bicycle module of the present invention, the timing at which the number of meshes of the planetary gears (each of the first planetary gears and each of the second planetary gears) changes can be made different by satisfying the above conditions. That is to say, the number of meshes of the respective planetary gears can be changed at different phases. Thereby capable of making planetary gears compared to conventional techniques The vibration when the number of meshes changes is reduced. That is to say, the vibration of the bicycle component can be reduced.

The bicycle assembly of the present invention can also be constructed as follows. In the bicycle assembly of the present invention, the sun gear further has a second sun gear. The second sun gear has a larger diameter than the first sun gear and meshes with the second planetary gear. Here, the value obtained by adding the number of teeth of the second sun gear to the number of teeth of the ring gear divided by the number of the second planetary gears is an integer. The number of teeth of the second sun gear and the number of teeth of the ring gear are different from the value of an integral multiple of the number of the second planetary gears.

When the condition is further increased, as in the case of the first planetary gear described above, the vibration at the time of the change in the meshing number of the second planetary gear can be further reduced. That is to say, the vibration of the bicycle component can be more effectively reduced.

The bicycle assembly of the present invention can also be constructed as follows. In the bicycle module of the present invention, the ring gear meshes with the first planetary gear.

The bicycle assembly of the present invention can also be constructed as follows. In the bicycle module of the present invention, the ring gear meshes with the second planetary gear.

The bicycle assembly of the present invention can also be constructed as follows. The bicycle assembly of the present invention further includes a hub axle and a control mechanism. A sun gear is provided on the hub axle. The control mechanism controls the sun gear to the first state and the second state. The first state is a state in which the sun gear is rotatable with respect to the hub axle. The second state is a state in which the sun gear is fixed with respect to the hub axle.

In the bicycle assembly of the present invention, the rotation of the hub shaft is input to the sun gear in the second state. Let the planets rotate by inputting to the sun gear The gear rotates. Also in this configuration, as described above, the vibration at the time of changing the meshing number of the planetary gear can be reduced. That is to say, the vibration of the bicycle component can be reduced.

The bicycle assembly of the present invention can also be constructed as follows. The bicycle assembly of the present invention further includes an electric motor. The output of the electric motor is input to one of the sun gear, the carrier, and the ring gear.

In the bicycle assembly of the present invention, the planetary gear is rotated by an electric motor. Also in this configuration, as described above, the vibration at the time of changing the meshing number of the planetary gear can be reduced. That is to say, the vibration of the bicycle component can be reduced.

With the present invention, the vibration of the bicycle component can be reduced.

14‧‧‧ Built-in variable speed hub

36‧‧·Wheel axle

160‧‧‧1st sun gear

164‧‧‧2nd sun gear

168‧‧‧3rd sun gear

172‧‧‧4th sun gear

300‧‧‧Sun Control Agency

420‧‧‧Motor

550, 128c‧‧‧1st planetary gear carrier

551, 128d‧‧‧1st ring gear

552, 129c‧‧‧2nd planetary gear carrier

553, 129d‧‧‧2nd ring gear

576, 128b‧‧‧1st planetary gear

608, 129b‧‧‧2nd planetary gear

Fig. 1 is a rear side view of a bicycle according to a first embodiment of the present invention.

Figure 2 is a cross-sectional view of the built-in shifting hub.

Figure 3 is an exploded perspective view of the built-in shifting hub.

Figure 4 is a partial cross-sectional view of the built-in shifting hub.

Figure 5 is a diagram showing the power transmission route of the built-in shifting hub.

Fig. 6 is a view showing the operation type of the control mechanism of the built-in shifting hub.

Fig. 7 is a schematic view showing the number of teeth and the number of teeth of each gear of the built-in shifting hub.

Fig. 8 is a schematic view showing the meshing state of the planetary gears.

Fig. 9A is a view showing a change in the meshing number of the planetary gear of the conventional built-in shifting hub.

Fig. 9B is a view showing a change in the number of meshing teeth of the planetary gear of the built-in shifting hub of the present invention.

Fig. 10 is a right side view showing the drive system of the electric assist bicycle according to the second embodiment of the present invention. Rear side view of the bicycle.

Figure 11 is a cross-sectional view of the drive unit.

Fig. 12 is a view showing the number of teeth and the number of teeth of each gear of the drive unit.

<First Embodiment>

Fig. 1 is a rear side view of the bicycle 10 according to the first embodiment of the present invention. A built-in shifting hub 14 (an example of a bicycle assembly) is assembled to the bicycle 10. The rear portion of the bicycle 10 includes a seat cushion tube 22 that supports the seat cushion 24, and a pair of chain brackets 26. The cushion tube 22 and the pair of chain brackets 26 are included in the frame 18.

The wheel 34 is rotatably supported by the frame 18 via the built-in shifting hub 14 at a portion where the chain bracket 26 and the seat cushion bracket 30 are connected. The crank assembly 38 is rotatably supported by the frame 18 at a connecting portion of the seat cushion tube 22 and the chain bracket 26.

The crank assembly 38 has a pedal 42 and a link 46. The chain 50 is engaged with the link 46. The chain 50 is wound around the sprocket 54. Sprocket 54 can be rotated The built-in shifting hub 14 is driven to the ground. The sprocket 54 is coupled to the built-in shifting hub 14. The control cable 61 is used to change the gear ratio of the built-in shifting hub 14. The control cable 61 is, for example, a Bowden type cable.

As shown in FIG. 2, the built-in shifting hub 14 includes a hub axle 36, a driving body 70, a hub cover 74, a power transmission mechanism 82, a coaster brake 86, and a shift/assist mechanism 90.

The hub axle 36 is fixed to a connecting portion of the chain bracket 26 and the seat cushion bracket 30. A plurality of groove portions as described below are formed in the hub axle 36. The solar control mechanism 300 is disposed in a plurality of grooves. For example, as shown in FIG. 3, the hub axle 36 has claw receiving grooves 264, 294, and 324, a sleeve groove 460, and arm grooves 464, 468, and 472. The first to third sun gear claws 207, 226, and 250, which will be described later, are disposed in the claw storage grooves 264, 294, and 324, respectively. A claw control sleeve 288, which will be described later, is disposed in the sleeve groove 460. The sleeve groove 460 is formed in the hub shaft 36 to be wide in the circumferential direction. The first to third claw control arms 284, 314, and 344, which will be described later, are disposed in the claw storage grooves 464, 468, and 472.

The drive body 70 is rotatably supported by the hub axle 36. As shown in FIG. 2, the driving body 70 is rotatably supported by the hub axle 36 via the ball bearing 98 and the roller bearing 102. The roller cone bearing 102 is held at a predetermined position by the actuating plate 104, the spacer 108, the washer 112, the non-rotatable lock washer 113, and the lock nut 114.

The hubcap 74 is rotatably supported by the hub axle 36. As shown in FIG. 2, the hubcap 74 has a spoke flange 78. A spoke is mounted on the spoke flange 78. A lamp cover portion 120 and a left cover portion 124 are disposed in the hub cover 74. The lamp cover portion 120 is non-rotatably embedded in the right side of the hub cover 74 Weekly. The left cover portion 124 is non-rotatably fitted to the left inner circumferential surface of the hub cover 74. The lamp cover portion 120 and the left cover portion 124 support the hub cover 74 so as to be rotatable about the hub axle 36.

As shown in Fig. 5, the power transmission mechanism 82 transmits rotational power from the driving body 70 to the hub cover 74 by a plurality of power transmission paths. As shown in FIG. 2 , the power transmission mechanism 82 includes a first sun gear 160 , a second sun gear 164 , a third sun gear 168 , a fourth sun gear 172 , and a solar control mechanism 300 .

As shown in FIG. 2, the first sun gear 160 is rotatably supported by the hub axle 36. The first sun gear 160 includes a clutch cam portion 176 and a plurality of first sun gear teeth 178 formed on the outer peripheral surface thereof.

As shown in FIGS. 2 to 4, the second sun gear 164 is disposed adjacent to the first sun gear 160 and is rotatably supported around the hub axle 36. The second sun gear 164 includes a plurality of first sun gear pawl teeth 206 , a first guide ring abutting surface 208 , and a plurality of second sun gear teeth 198 .

As shown in FIGS. 2 to 4, the third sun gear 168 is disposed adjacent to the second sun gear 164 and is rotatably supported around the hub axle 36. The third sun gear 168 includes a second guide ring abutting surface 220 , a plurality of second sun gear ratchet teeth 224 , a third guide ring abutting surface 228 , and a plurality of third sun gear teeth 236 .

As shown in FIGS. 2 to 4, the fourth sun gear 172 includes a plurality of fourth sun gear teeth 244 and a plurality of third sun gear pawl teeth. 248 and the fourth guide ring abutting surface 252.

As shown in FIG. 3, the solar control mechanism 300 (an example of a control mechanism) controls the rotation of the second sun gear 164, the third sun gear 168, and the fourth sun gear 172. The solar control mechanism 300 includes a first sun gear pawl 207, a second sun gear pawl 226, a third sun gear pawl 250, and a pawl control sleeve 288. The first sun gear pawl 207 is rotatably disposed in the pawl housing groove 264 of the hub axle 36 and is engaged with the first sun gear pawl tooth 206. The second sun gear pawl 226 is rotatably disposed in the pawl receiving groove 294 of the hub axle 36 and is engaged with the second sun gear pawl tooth 224. The third sun gear pawl 250 is rotatably disposed in the pawl housing groove 324 of the hub axle 36 and is engaged with the third sun gear pawl tooth 248. The first sun gear pawl 207, the second sun gear pawl 226, and the third sun gear pawl 250 are biased toward the outer peripheral side by the springs 272, 302, and 332, respectively.

The claw control sleeve 288 controls the engagement of the first to third sun gear claws 207, 226, and 250 with the first to third sun gear pawl teeth 206, 224, and 248, respectively. The claw control sleeve 288 includes a base portion 408, a first claw control arm 284, a second claw control arm 314, and a third claw control arm 344. The base portion 408 is disposed in the sleeve groove 460 of the hub axle 36. In this state, the base portion 408 is rotatable about the hub axle 36. The outer peripheral portion of the base portion 408 is supported by a first sun gear guide ring 210, a second sun gear guide ring 234, and a third sun gear guide ring 258 which will be described later. The first claw control arm 284, the second claw control arm 314, and the third claw control arm 344 are disposed in the arm grooves 464, 468, and 472 of the hub axle 36, respectively.

When the pawl control sleeve 288 is rotated, the engagement state of the first to third sun gear claws 207, 226, and 250 with the first to third sun gear pawl teeth 206, 224, and 248 is changed. For example, in a state where the first sun gear pawl 207 and the first sun gear pawl tooth 206 are not engaged (an example of the first state), the second sun gear 164 can rotate with respect to the hub axle 36. The same applies to the state in which the second sun gear pawl 226 and the second sun gear pawl tooth 224 are not engaged. The same applies to the state in which the third sun gear pawl 250 and the third sun gear pawl tooth 248 are not engaged. On the other hand, in a state in which the first sun gear pawl 207 and the first sun gear pawl tooth 206 are not engaged (an example of the second state), the second sun gear 164 cannot rotate with respect to the hub axle 36. The same applies to the state in which the second sun gear pawl 226 is engaged with the second sun gear pawl tooth 224. The same applies to the state in which the third sun gear pawl 250 is engaged with the third sun gear pawl teeth 248. Whether the second to fourth sun gears 164, 168, and 172 are rotatable with respect to the hub axle 36 is controlled at each speed stage as shown in Fig. 6.

As shown in FIGS. 2 to 4 , the power transmission mechanism 82 further includes a first sun gear guide ring 210 , a second sun gear guide ring 234 , and a third sun gear guide ring 258 . One half of the first sun gear guide ring 210 is fitted between the first guide ring abutting surface 208 of the second sun gear 164 and the hub axle 36. The other half of the first sun gear guide ring 210 is fitted between the second guide ring abutting surface 220 of the third sun gear 168 and the hub axle 36. The second sun gear guide ring 234 is fitted between the third guide ring abutting surface 228 of the second sun gear 164 and the hub axle 36 . The third sun gear guide ring 258 is fitted into the fourth guide ring abutting surface of the fourth sun gear 172 252, between the hub axle 36.

As shown in FIG. 2, the power transmission mechanism 82 further includes a first planetary gear carrier 550 (an example of a carrier), a first ring gear 551 (an example of a ring gear), and a second planetary gear carrier 552 ( An example of the carrier), a second ring gear 553 (an example of a ring gear), a plurality of first planetary gears 576, and a plurality of second planetary gears 608. Here, the first planetary gear carrier 550, the first ring gear 551, the second planetary gear carrier 552, and the second ring gear 553 are attached so as to be rotatable around the hub axle 36.

The first ring gear 551 has a first inner circumferential gear portion 585 and a second inner circumferential gear portion 586. The first inner circumference gear portion 585 is spline-engaged with the large diameter gear portion 584. The second inner circumference gear portion 586 is engaged with the one-way clutch 587. The one-way clutch 587 generates a function between the driving body 70 and the first ring gear 551.

The first planetary gear carrier 550 rotatably supports a plurality of (for example, three) first planetary gears 576 around the rotation axis of the first sun gear 160. The first planetary gear carrier 550 has a plurality of first planetary gear support pins 572. The first planetary gear support pin 572 rotatably supports the first planetary gear 576. The right end portion of the first planetary gear carrier 550 is spline-engaged with the clutch ring 562. The left end portion of the first planetary gear carrier 550 is spline-engaged to the right end portion of the second planetary gear carrier 552.

The second planetary gear carrier 552 rotatably supports a plurality of (for example, three) second planetary gears 608 around the rotation axes of the second sun gear 164 and the third sun gear 168. The second planetary gear carrier 552, There are a plurality of second planetary gear support pins 604. The second planetary gear support pin 604 rotatably supports the second planetary gear 608. The right end portion of the second planetary gear carrier 552 is spline-engaged with the left end portion of the first planetary gear carrier 550. The left end portion of the second planetary gear carrier 552 is engaged with the brake roller frame 597 and the plurality of brake rollers 900 in the coaster 86.

The second ring gear 553 has a third inner circumferential gear portion 624. The third inner circumference gear portion 624 is spline-engaged with the small diameter gear portion 620. The second ring gear 553 is coupled to the lamp cover portion 120 via a one-way clutch 628 . In other words, the second ring gear 553 is coupled to the hub cover 74 via the one-way clutch 628 and the lamp cover portion 120. The one-way clutch 587 functions between the hub cover 74 (the lamp cover portion 120) and the second ring gear 553.

As shown in Fig. 2, the first planetary gear 576 is a two-stage stepped planetary gear. The first planetary gear 576 includes a small-diameter gear portion 580 (an example of a first planetary gear or a second planetary gear) and a large-diameter gear portion 584 (an example of a second planetary gear or a first planetary gear).

The small-diameter gear portion 580 is spline-engaged with the first sun gear teeth 178 of the first sun gear 160. The number of teeth of the small-diameter gear portion 580 is a value that is an integral multiple of the number of the first planetary gears 576. For example, when the number of the first planetary gears 576 is three, the number of teeth of the small-diameter gear portion 580 is 15T (refer to FIG. 7). ).

The large diameter gear portion 584 is spline-engaged with the first inner circumferential gear portion 585 of the first ring gear 551. The number of teeth of the large diameter gear portion 584 is a value that is an integral multiple of the number of the first planetary gears 576, for example, the number of the first planetary gears 576. When the amount is three, the number of teeth of the large diameter gear portion 584 is 24T (refer to Fig. 7).

Here, the first sun gear 160, the first planetary gear 576, and the first ring gear 551 described above satisfy the following condition A.

Condition A: The value obtained by dividing the number of teeth of the first sun gear 160 and the number of teeth of the first ring gear 551 by the number of the first planetary gears 576 is an integer. The number of teeth of the first sun gear 160 and the number of teeth of the first ring gear 551 are different from the value of an integral multiple of the number of the first planetary gears 576.

For example, as shown in FIG. 7, the number of teeth of the first sun gear 160 is 46T, the number of teeth of the first ring gear 551 is 83T, and the number of the first planetary gears 576 is three, and the number of teeth of the first sun gear 160 is The total number of teeth of the first ring gear 551 (46 + 83 = 129) divided by the number of the first planetary gears 576 is an integer (129/3 = 43). In this case, the number of teeth of the first sun gear 160 (=46) and the number of teeth of the first ring gear 551 (83) are different from the values of the integral multiple of the number (=3) of the first planetary gears 576.

By conforming to the above-described condition A, as shown in FIGS. 8 and 9B, the timing at which the number of meshing of the first planetary gear 576 and the first sun gear 160 and the first ring gear 551 is changed can be different. In other words, the number of meshing of each of the first planetary gears 576 can be changed in different phases. Thereby, the vibration at the time of changing the meshing number of the first planetary gears 576 can be reduced. That is to say, the vibration of the built-in shifting hub 14 can be reduced.

Here, FIG. 8 is a view showing a state in which the first planetary gear 576 is meshed with the first ring gear 551. Figure 9B is the first planetary gear 576 and A display diagram of the number of meshing teeth between the first ring gears 551. The first planetary gear 576 is also meshed in the same manner as the first sun gear 160.

As shown in Fig. 2, the second planetary gear 608 is a three-stage stepped planetary gear. The second planetary gear 608 includes a large diameter gear portion 612 , a middle diameter gear portion 616 , and a small diameter gear portion 620 . The large diameter gear portion 612 is meshed with the plurality of fourth sun gear teeth 244 of the fourth sun gear 172. The middle diameter gear portion 616 is meshed with the plurality of third sun gear teeth 236 of the third sun gear 168. The small diameter gear portion 620 is meshed with the plurality of second sun gear teeth 198 of the second sun gear 164. The number of teeth of the large diameter gear portion 612, the number of teeth of the middle diameter gear portion 616, and the number of teeth of the small diameter gear portion 620 are determined in accordance with the required gear ratio. The number of teeth of the large diameter gear portion 612, the number of teeth of the middle diameter gear portion 616, and the number of teeth of the small diameter gear portion 620 may be selected as a value that is an integral multiple of the number of the second planetary gears 608.

Here, the first sun gear 160, the first planetary gear 576, and the first ring gear 551 described above satisfy the following condition B.

Condition B: The value obtained by dividing the number of teeth of the second sun gear 164 and the number of teeth of the second ring gear 553 by the number of the second planetary gears 608 is an integer. The number of teeth of the second sun gear 164 and the number of teeth of the second ring gear 553 are different from the value of an integral multiple of the number of the second planetary gears 608. For example, as shown in FIG. 7, the number of teeth of the second sun gear 164 is 49T, the number of teeth of the second ring gear 553 is 80T, the number of the second planetary gears 608 is three, and the number of teeth of the second sun gear 164 is The total number of teeth of the second ring gear 553 (49 + 80 = 129) divided by the number of the second planetary gears 608 is an integer (129/3 = 43). In this case, the second sun gear The number of teeth (=49) of 164 and the number of teeth (80) of the second ring gear 553 are different from the values of integer multiples of the number (=3) of the second planetary gears 608, respectively.

The value obtained by dividing the number of teeth of the third sun gear 168 and the number of teeth of the second ring gear 553 by the number of the second planetary gears 608 is an integer. The number of teeth of the third sun gear 168 and the number of teeth of the second ring gear 553 are different from the value of an integral multiple of the number of the second planetary gears 608. For example, the number of teeth of the third sun gear 168 is 40T, the number of teeth of the second ring gear 553 is 80T, the number of the second planetary gears 608 is three, the number of teeth of the third sun gear 168 and the second ring gear 553 The total number of teeth (40 + 80 = 120) divided by the number of second planetary gears 608 is an integer (120 / 3 = 40). In this case, the number of teeth of the second sun gear 164 (=40) and the number of teeth of the second ring gear 553 (=80) are different from the values of the integral multiple of the number (=3) of the second planetary gears 608.

The value obtained by dividing the number of teeth of the fourth sun gear 172 and the number of teeth of the second ring gear 553 by the number of the second planetary gears 608 is an integer. The number of teeth of the fourth sun gear 172 and the number of teeth of the second ring gear 553 are different from the value of an integral multiple of the number of the second planetary gears 608. For example, the number of teeth of the fourth sun gear 172 is 34T, the number of teeth of the second ring gear 553 is 80T, the number of the second planetary gears 608 is three, and the number of teeth of the fourth sun gear 172 and the second ring gear 553. The total number of teeth (34 + 80 = 114) divided by the number of second planetary gears 608 is an integer (114 / 3 = 38). In this case, the number of teeth of the fourth sun gear 172 (=32) and the number of teeth of the second ring gear 553 (=80) are respectively the second The value of the integral multiple of the number (=3) of the planetary gears 608 is different.

By conforming to the above condition B, as shown in Figs. 8 and 9B, the number of meshes of the second planetary gear 608 and the second to fourth sun gears 164, 168, 172 and the second ring gear 553 can be changed. The timing is different. In other words, the number of meshing of each of the second planetary gears 608 can be changed in different phases. Thereby, the vibration at the time of changing the meshing number of the second planetary gear 608 can be reduced. That is to say, the vibration of the built-in shifting hub 14 can be reduced.

Here, Fig. 8 is a view showing a state in which the second planetary gear 608 is meshed with the second ring gear 553. FIG. 9B is a view showing the number of meshing teeth between the second planetary gear 608 and the second ring gear 553. The second planetary gears 608 are also meshed in the same manner as the second to fourth sun gears 164, 168, and 172.

In the relationship between the large diameter gear portion 612 and the middle diameter gear portion 616, the large diameter gear portion 612 is an example of the first planetary gear or the second planetary gear, and the middle diameter gear portion 616 is the second planetary gear or the first planetary gear. An example of this. In the relationship between the intermediate diameter gear portion 616 and the small diameter gear portion 620, the middle diameter gear portion 616 is an example of the first planetary gear or the second planetary gear, and the small diameter gear portion 620 is the second planetary gear or the first planetary gear. An example of this. Further, in the relationship between the large diameter gear portion 612 and the small diameter gear portion 620, the large diameter gear portion 612 is an example of the first planetary gear or the second planetary gear, and the small diameter gear portion 620 is the second planetary gear or the first planetary gear. An example of a gear.

The shift/assist mechanism 90 is for controlling the connection of the driving body 70 and the power transmitting mechanism 82. As shown in Fig. 2, the shift/assist mechanism 90 has a change Key member 700. The shift key member 700 is moved along the clutch cam portion 176 of the first sun gear 160 to open and close the engagement of the clutch ring 562 and the first planetary gear carrier 550. When the shift key member 700 is at the position of FIG. 2, the clutch ring 562 is engaged with the first planetary gear carrier 550, and the drive body 70, the clutch ring 562, and the first planetary gear carrier 550 are rotated as one unit. On the other hand, when the shift key member 700 is moved from the position of the second figure to the right side, the engagement of the clutch ring 562 with the first planetary gear carrier 550 is released. That is, the connection between the driving body 70 and the first planetary gear carrier 550 is released. For example, as shown in FIG. 6, the engagement state of the driving body 70 and the clutch ring 562, and the second to fourth sun gears 164, 168, and 172 and the first to third sun gear claws 207, 226, and 250 are formed. The engagement state determines the gear ratio of each speed stage.

The Coaster Brake 86 is used to prevent relative rotation of the hub cover 74 with respect to the hub axle 36. The Coaster Brake 86 is supported so as not to be rotatable about the hubcap 74. The Coaster Brake 86 operates by rotating the sprocket 54 in the opposite direction. The spline of the clutch ring 562 and the spline of the first planetary gear 550 are tapered. As a result, when the clutch ring 562 is engaged with the first planetary gear carrier 550, the sprocket 54 rotates in the opposite direction, and when the coaster brake 86 is operated, the clutch ring 562 is disengaged from the first planetary gear carrier 550. . Thereby, when the coaster brake 86 is actuated, the built-in shifting hub 14 is driven by the "drive body 70 → one-way clutch 587 → the first ring gear 551 → the first planetary gear at any speed stage Carrier 550 → 2nd planetary gear carrier 552 → brake roller 900→The route of the coaster 86→the hubcap 74” is reversed to convey the rotational force of the driver 70.

<Second Embodiment>

Fig. 10 is a right side view showing an example of a drive system of the electric assist bicycle according to the second embodiment of the present invention. A drive unit 301 (an example of a bicycle assembly) is incorporated in the electric assist bicycle. The electric assist bicycle transmits the pedaling force acting on the pedal 400 via a route such as a crank arm 401 → a crankshaft 402 → a driving unit 301 → a front sprocket 403 → a chain 404 → a rear sprocket 405 The hub body on which the axle 406 of the rear wheel rotates. In this process, the electric assist bicycle combines the output of the motor 420 into auxiliary power to assist in traveling.

In the power-assisted bicycle, the force generated by the torque acting on the crankshaft 402 is detected by the inductor portion 450 (described later). In the power-assisted bicycle, when the detected value of the sensor unit 450 exceeds the set value, the motor 420 (described later) is activated to generate a torque corresponding to the pedaling force as the assisting power. The drive unit 301 including the motor 420 is disposed in the vicinity of the connection portion between the lower end portion of the seat cushion tube of the frame of the electric assist bicycle and the rear end portion of the lower tube of the frame. The battery for driving the motor is disposed, for example, along a seat tube.

As shown in FIG. 11, the drive unit 301 is provided with a casing 111, a motor 420 (an example of an electric motor), an inductor unit 450, a power transmission mechanism 131, and a speed reduction mechanism 127. The housing 111 has a through hole 111a. The crankshaft 402 is inserted through the through hole 111a. The crankshaft 402 is rotatably supported by the casing 111 via bearings 112 and 113. in Two crank arms 401 are detachably mounted at both ends of the crankshaft 402.

The motor 420 has its rotating shaft disposed coaxially with the rotating shaft of the crankshaft 402. The motor 420 has a motor housing 125, a stator 121, and a rotor 123. The motor housing 125 is fixed to the housing 111. A hole portion 120a in which the crank shaft 402 can be disposed is formed in the motor housing 125. The stator 121 is formed in a cylindrical shape and is disposed on a concentric circle of the crankshaft 402. The stator 121 is fixed to the motor housing 125. The rotor 123 is formed in a cylindrical shape and is disposed on the outer peripheral portion of the stator 121. The rotor 123 is rotatably supported by the motor housing 125. The rotor 123 has, for example, a magnet (not shown) having a plurality of magnetic poles in the circumferential direction, and a magnet holding portion (not shown) for holding the magnet.

The motor 420 is driven by an inverter (not shown). The inverter is driven by a control unit (not shown), and the control unit controls the inverter in response to the pedaling force and the speed of the bicycle.

The inductor portion 450 detects the torque acting on the crankshaft 402. This torque is proportional to the pedaling force of the user applied to the crankshaft 402. By detecting this torque, the pedaling force of the user acting on the crankshaft 402 is detected. The inductor portion 450 is disposed between the motor 420 and the crankshaft 402 inside the hole portion 120a. The inductor portion 450 has a hollow member 151 and a strain sensor 155. The hollow member 151 has an insertion hole in which the crank shaft 402 can be disposed. The strain sensor 155 is a magnetostrictive inductor. The strain sensor 155 has a magnetostrictive element 155a and a detecting coil 155b provided around the magnetostrictive element 155a. The magnetostrictive element 155a is fixed to the hollow member 151. The detection coil 155b is fixed to the motor housing 125. That is, the detecting coil 155b is rotatably supported by the casing 111. The magnet acting on the crankshaft 402 is detected by the magnetostrictive element 155a and the detecting coil 155b.

The power transmission mechanism 131 transmits the rotational force of the motor 420 and the rotational force of the crankshaft 402 to the front sprocket 403. The power transmission mechanism 131 is provided on one end side of the crankshaft 402. The power transmission mechanism 131 is formed in a ring shape. The power transmission mechanism 131 is coupled to the torque transmission member 130 via the one-way clutch 132. In other words, the torque transmission member 130 is rotatably supported by the power transmission mechanism 131 via the one-way clutch 132. The torque transmission member 130 is coupled to the speed reduction mechanism 127. Here, the torque transmission member 130 is integrally formed with the second planetary gear carrier 129c (described later) of the speed reduction mechanism 127.

The power transmission mechanism 131 is rotatably supported by the casing 111 via bearings 113 and 134. The end of the power transmission mechanism 131 protrudes from the opening 111b of the casing 111 to the outside. The front sprocket 403 is detachably attached to the protruding portion by, for example, a bolt. Thereby, the front sprocket 403 can be rotated integrally with the power transmission mechanism 131. The power transmission mechanism 131 is fixed to the hollow member 151. Thereby, the power transmission mechanism 131 can rotate integrally with the crankshaft 402.

The speed reduction mechanism 127 transmits the output of the motor 420 to the torque transmitting member 130. For example, the speed reduction mechanism 127 transmits the rotation of the rotor 123 to the torque transmitting member 130. The speed reduction mechanism 127 has more than one gear.

The speed reduction mechanism 127 includes a first sun gear 128a (an example of a sun gear), a plurality of first planetary gears 128b (an example of a planetary gear), and a first planetary gear carrier 128c (an example of a carrier) The first ring gear 128d (an example of a ring gear).

The first sun gear 128a is coupled to a motor 420 such as a rotor 123. That is, the output of the motor 420 is input to the first sun gear 128a. The plurality of (for example, three) first planetary gears 128b are disposed between the first sun gear 128a and the first ring gear 128d, and are spline-engaged with the first sun gear 128a and the first ring gear 128d. As shown in Fig. 12, the number of teeth of the first planetary gears 128b is an integral multiple of the number of the first planetary gears 128b. For example, when the number of the first planetary gears 128b is three, the number of teeth of the first planetary gears 128b is 15T. The first planetary gear carrier 128c rotatably supports a plurality of first planetary gears 128b. The first ring gear 128d is fixed to the casing 111.

Here, the first sun gear 128a, the first planetary gear 128b, and the first ring gear 128d described above satisfy the following condition C.

Condition C: The value obtained by dividing the number of teeth of the first sun gear 128a and the number of teeth of the first ring gear 128d by the number of the first planetary gears 128b is an integer. The number of teeth of the first sun gear 128a and the number of teeth of the first ring gear 128d are different from the value of an integral multiple of the number of the first planetary gears 128b.

For example, as shown in Fig. 12, the number of teeth of the first sun gear 128a is 49T, the number of teeth of the first ring gear 128d is 80T, and the number of the first planetary gears 128b is three, and the number of teeth of the first sun gear 128a is The total number of teeth (49 + 80 = 129) of the first ring gear 128d divided by the number of the first planetary gears 128b is an integer (129/3 = 43). In this case, the number of teeth (=49) of the first sun gear 128a and the first ring gear The number of teeth (=80) of the wheel 128d is different from the value of an integral multiple of the number (=3) of the first planetary gears 128b.

The speed reduction mechanism 127 further includes a second sun gear 129a (an example of a sun gear), a plurality of second planetary gears 129b (an example of a planetary gear), a second planetary gear carrier 129c (an example of a carrier), and a second ring. Gear 129d (an example of a ring gear). The second sun gear 129a is coupled to the first planetary gear carrier 128c. The plurality of (for example, three) second planetary gears 129b are disposed between the second sun gear 129a and the second ring gear 129d, and are spline-engaged with the second sun gear 129a and the second ring gear 129d. As shown in Fig. 12, the number of teeth of the second planetary gear 129b is an integral multiple of the number of the second planetary gears 129b. For example, when the number of the second planetary gears 129b is three, the number of teeth of the second planetary gears 129b is 15T. The second planetary gear carrier 129c rotatably supports a plurality of second planetary gears 129b. The second ring gear 129d is fixed to the casing 111.

Here, the second sun gear 129a, the second planetary gear 129b, and the second ring gear 129d described above satisfy the following condition D.

Condition D: The value obtained by dividing the number of teeth of the second sun gear 129a and the number of teeth of the second ring gear 129d by the number of the second planetary gears 129b is an integer. The number of teeth of the second sun gear 129a and the number of teeth of the second ring gear 129d are different from the value of an integral multiple of the number of the second planetary gears 129b.

For example, as shown in Fig. 12, the number of teeth of the second sun gear 129a is 49T, and the number of teeth of the second ring gear 129d is 80T, the second planetary gear When the number of 129b is three, the total number of teeth of the second sun gear 129a and the number of teeth of the second ring gear 129d (49+80=129) divided by the number of the second planetary gears 129b is an integer (129/) 3=43). In this case, the number of teeth of the second sun gear 129a (=49) and the number of teeth of the second ring gear 129d (=80) are different from the values of the integral multiple of the number (=3) of the second planetary gears 129b.

The output of the speed reduction mechanism 127 is transmitted from the second planetary gear carrier 129c to the torque transmitting member 130. Here, the torque transmission member 130 is formed integrally with the second planetary gear carrier 129c. The output of the speed reduction mechanism 127 is transmitted to the power transmission mechanism 131 via the torque transmission member 130.

The drive unit 301 transmits the torque caused by the pedaling force of the rider to: the crank arm 401 → the crankshaft 402 → the hollow member 151 → the power transmission mechanism 131 . The output torque from the motor 420 is transmitted to the speed reduction mechanism 127 → the torque transmission member 130 → the one-way clutch 132 → the power transmission mechanism 131. The power transmission unit 131 combines the two types of torques and transmits the combined torque to the front sprocket 403. This achieves the assistance of the motor.

In the drive unit 301 having the above configuration, the number of teeth of the first planetary gears 128b and the number of teeth of the second planetary gears 129b are integer multiples of the number of the first planetary gears 128b and the number of the second planetary gears 129b, respectively. The drive unit 301 meets the above condition C and condition D. As shown in FIGS. 8 and 9B, the vibration when the number of meshing of the first planetary gear 128b and the second planetary gear 129b is changed can be reduced. The vibration of the drive unit 301 can be reduced.

Figure 8 is a view showing that the first and second planetary gears 128b and 129b are engaged 1 and a display diagram of the positions of the second ring gears 128d and 129d. Fig. 9B is a view showing the number of meshing of the first and second planetary gears 128b and 129b and the first and second ring gears 128d and 129d. The first and second planetary gears 128b and 129b are also meshed in the same manner as the first and second sun gears 128a and 129a.

<Other Embodiments>

(a) In the first and second embodiments, the number of teeth of the first planetary gears 576 and 128b and the second planetary gears 608 and 129b is an integral multiple of the number of the planetary gears 576, 608, 128b, and 129b. An example of the situation. However, if the conditions (conditions A to D) shown in the first and second embodiments are satisfied, the number of teeth of the first planetary gears 576 and 128b and the second planetary gears 608 and 129b does not necessarily need to be a planetary gear. A value that is an integer multiple of the number of 576, 608.

(b) In the above-described first embodiment, an example in which all of the second to fourth sun gears 164, 168, and 172 meet the condition B is displayed, and even the second to fourth sun gears 164, 168, and 172 are displayed. Any one that meets the above condition B can expect the above effects.

(c) In the first embodiment described above, the eight-stage built-in shifting hub is shown, and the number of stages is not limited to eight, and the present invention can be applied as long as it is a built-in shifting hub having a planetary gear mechanism. And even if you don't have a coaster (Coaster Brake).

(d) in the first and second embodiments, the sun gear, the planetary gear set, and the at least one set of the planetary gear mechanisms are meshed with each other The ring gear, the number of teeth of the sun gear and the number of teeth of the ring gear are added by the value of the number of planetary gears, and the number of teeth of the sun gear and the number of teeth of the ring gear are integer multiples of the number of the planetary gears. If the values are different, the configuration of the other planetary gear mechanisms may be different.

(e) In the first and second embodiments, the bicycle shifting hub 14 and the drive unit 301 are used as an example of the bicycle unit, and the planetary gear mechanism (sun gear, planetary gear, The bicycle assembly of the ring gear and the carrier can be applied to other bicycle components.

160‧‧‧1st sun gear

164‧‧‧2nd sun gear

168‧‧‧3rd sun gear

172‧‧‧4th sun gear

550‧‧‧1st planetary gear carrier

551‧‧‧1st ring gear

552‧‧‧2nd planetary gear carrier

553‧‧‧2nd ring gear

576‧‧‧1st planetary gear

580‧‧‧ Small diameter gear

584‧‧‧ Large diameter gear

608‧‧‧2nd planetary gear

612‧‧‧ Large diameter gear

616‧‧‧Medium diameter gear

620‧‧‧ Small diameter gear

Claims (13)

A bicycle assembly comprising: a sun gear, a plurality of planetary gears, a ring gear, and a carrier; the plurality of planetary gears meshing with the sun gear; the ring gear meshing with the plurality of the planetary gears; the carrier is wound around The rotating shaft of the sun gear is rotatably held by the planetary gear; the value of the number of teeth of the sun gear is increased by the value of the number of teeth of the ring gear divided by the number of the planetary gears; and the number of teeth of the sun gear and The number of teeth of the ring gear is different from the value of an integral multiple of the number of the planetary gears. The bicycle component according to claim 1, wherein the number of the planetary gears is three. The bicycle unit according to claim 1 or 2, wherein the number of teeth of the planetary gear is a value that is an integral multiple of the number of the planetary gears. The bicycle unit according to claim 1, wherein the planetary gear includes: a first planetary gear and a second planetary gear; the second planetary gear has a larger diameter than the first planetary gear; and the sun gear has a first sun a gear, the first sun gear meshes with the first planetary gear; a value obtained by adding a number of teeth of the first sun gear to a number of teeth of the ring gear divided by a number of the first planetary gears is an integer; 1 the number of teeth of the sun gear and the number of teeth of the ring gear, and the first line The value of the integer multiple of the number of star gears is different. A bicycle module according to claim 4, wherein the ring gear meshes with the first planetary gear. A bicycle module according to claim 4, wherein the ring gear meshes with the second planetary gear. The bicycle assembly according to any one of claims 4 to 6, wherein the sun gear further has a second sun gear; the second sun gear has a smaller diameter than the first sun gear and meshes with the second planet a gear; a value obtained by adding a number of teeth of the second sun gear to the number of teeth of the ring gear divided by a value of the number of the first planetary gears; and a number of teeth of the second sun gear and a number of teeth of the ring gear; The value is different from the value of an integral multiple of the number of the second planetary gears. The bicycle unit according to claim 1, wherein the planetary gear includes: a first planetary gear and a second planetary gear; the second planetary gear has a smaller diameter than the first planetary gear; and the sun gear has a first sun a gear, the first sun gear meshes with the first planetary gear; a value obtained by adding a number of teeth of the first sun gear to a number of teeth of the ring gear divided by a number of the first planetary gears is an integer; The number of teeth of the sun gear and the number of teeth of the ring gear are different from the value of an integral multiple of the number of the first planetary gears. The bicycle unit according to claim 8, wherein the ring gear meshes with the first planetary gear. The bicycle unit according to claim 8, wherein the ring gear meshes with the second planetary gear. The bicycle assembly according to any one of claims 8 to 10, wherein the sun gear further has a second sun gear; the second sun gear has a diameter larger than the first sun gear and meshes with the second planet a gear; a value obtained by adding a number of teeth of the second sun gear to the number of teeth of the ring gear divided by a value of the number of the first planetary gears; and a number of teeth of the second sun gear and a number of teeth of the ring gear; The value is different from the value of an integral multiple of the number of the second planetary gears. A bicycle module according to claim 1, further comprising a hub axle and a control mechanism; wherein the sun gear is provided with the sun gear; and the control mechanism controls the sun gear to a first state and a second state The first state is a state in which the sun gear is rotatable with respect to the hub axle, and the second state is a state in which the sun gear is fixed to the hub axle. The bicycle unit according to claim 1, further comprising an electric motor, wherein an output of the electric motor is input to one of the sun gear, the carrier, and the ring gear.